Speed responsive fluid control means



'Jan- 1, 1957 D. c. WxLKl-:RsoN 2,775,910

SPEED RESPONSIVE FLUID CONTROL MEANS Jan. 1, 1957 D. c. wlLKERsoN 2,775,910

SPEED RESPONSIVE ELUIO CONTROL MEANS Filed Jan. 15, 1951 4 Sheet'S-Sheet 2 'Mik Gttornegs Jan. 1, 1957 D. c. wlLKERsoN 2,775,910

SPEED RESPONSIVE FLUID CONTROL MEANS Filed Jan. 15, 1951 4 Sheets-Sheet .'5

500 lOOO |500 LY-M Cmrncgls Jan. 1, 1957 D. c. wlLKERsoN SPEED RESPONSIVE FLUID CONTROL MEANS 4 Sheets-Sheet 4 Filed Jan. l5, 1951 :inventor @zak/W/ew//z E 7% United States Patent() l 'control systerisy characterized SPEED RESPNSIV FLUID' GON'ERGB 5 Danieicayle wir maintien', Mieli., rssigqrfu'':

eralMotr's Corporation, Detrit, of Delaware Application-January is, i951; serial Nmzisr sis-claims; (ci. idr-Jsfi This invention relates to transmissions and morepar'- ticularly to control systems for step-ratio transmissions of the type' having fluid pressure actuatedservomotorsifor selectively choosing the gear ratio of the transmission-t The invention' contemplates the use'of aJ novely forni' of valve responsive touid pressure and/or centrifugal' force for regulating the torque capacity of ratio-changing# friction members in a step-ratio' transmissiolif and for regulating the torque capacity of fr'ictioril clutch members g'en'- erally. .Y

Various types' of valves' have heretofore beenI employed for the purposes set forth above, but suchF valvesliav not been entirely satisfactory for ay vari'ety of reasop's For example, many of the valves formerly erriployed in such systems have been found to inherently embod'yun'desirable performance characteristics; while all such" valves have been extremely expensive iri that niuch cr'eful a'nd accurate machining is necessary to obtain a permissible standard of performance. Valves constructediiiY accordance-with the teachings of this inventioir are foundt" be ,35

very inexpensive" and highly satisfactoryv iiir control syster'ns provided the'y are selected" for use" ingccrdane with the orice andy pressure" values required' by the system.

By this invention a' simple coil spring isJ utilized as a val've. The utility of the coil springas' aivalv' based o`n the fact that present-day springs are manufacturedfof i standardized materials, are heat-treated' nd processed' and formed ori automatic machines with ahi'gh dgree'of` ac'- curacy, such that their stress' responsesdovetail with the requirementsfo'r valve action; esp'eciall-y inL dynamic pressure systems in which a small amount' of constant l'ea-lca'gei is not only permissible' but highly dsirable' for lter.- c'olin'g, and" lubrication circulation; Heretbfor coil springs have been made by lssaccurat'po'cssingr and. were" iit adaptable' to th'euses set forth herein?. The present-day commercial coil spring is; however,1 eiently ace 'ate i'n its" physicalproperties toperfonbthe werk outlined this specification, provi-dedE it-i's duly giiidd to" maintain ts aitial relationshipunierdllctioi.

Anf object' of thisVA invention is toproviue atraiismrsson drive control system incorporating a novel valveiprticiriny adapted-for use in uuid' pressure entrer systeiris v ATt further objet of` this invent" to' previas.` in a transmission control' system-incorpor ting-E a-Liiid' pressure Servo mechanism? agli novel coil: Spring VlvY foi" gu'lafilig iiui'cl pressuresupp'lid to the servdrinsl Another object of this invention' isv valve for regulating' Huid p'r'e'ssue and' s"elf-c leariirigA featurewlire y p "A l r u stirred' and` undesirable staking f the viv' ail t'd'relga matter is prevented;d p l .l A

An additional object o f this inventionI `to prvidka. coil spring v alve in which tension in the coils. may be readily and simply adjusted as maybe desiredi.d

unen., af ernennen 0 v-ius novel valve particularly adapted for use in transmission 2,775,910 Fatented .la-m l; 1957 by its long serviceable life, trouble free performance,` and economy of manufacture.

A further object ofths invention is to provide in a transmission control system a `valve structure for controlfling lluid pressure suppliedto the transmission servo members and in which the valve is responsive to speed of rotation 4and to inertia effects due to acceleration and deceleration o`f thef speed of rotation of the valve,` the inertia effect being zslipenirrrpose'd upon the speed elect and decreasing with increase` inA speed, but increasing with decreasein speed'o rotation of the valve.

These and many other objects of this invention will' be `ap'parentefrorn the following description and claims,- taken 'in conjunction with thel accompanying drawings, lin which:

Figure l is a longitudinaly section of a transmission incorporating-a; Yvalve constructed in accordance with the principlesof this invention.

Figure' 2 isa view of the assembly of Figure l broken away from part sections to show the device control elements.`

Figure 3 is a schematic diagram of control plumbing and valve arrangement for Vactivating the fluid pressure servos of theclutches and brakes.

Figure 4 illustrates one form of pressure regulator Valve in section, the valve being in o'pen position;

Figurej4'a is a view similar to Figure 4 illustrating the valve of Figure 4 in closed position.

Figure 4b is a grap'h illustrating the operation of the structure of Figures 4, 4a showing the relationship between speed and pressure rise in the passages connected to the-inlet port of the pressure regulator valve illustrated therein;

Figure 5 isa sectional view of a modified form of valve vin which the hi'gh pressure is applied external 'of the spring valve. A

l Figureea `illustrates a modified version of the 4valve showninrFigure 5 in which the external plug-may be used kas a` spring tension adjuster.

Figure 5b is a plan View of the valve 'shown in Figure 5a illustrating the end plu'g and retaining means whereby the 'end plug may be fixed against rotation upon adjustment of the tension Vof the spring valve `of Figui'e 5a;

Figure 5c is a sectional view of an alternate arrang- 4ment for preventing -rotary motion of the valve plug within the casing upon the application of tension tb the kspring valve; which arrangement may be substituted for that illustrated in Figure 5a. A

j Figure -Sd -is a se'ctional View illustrating a modification of -thevalve shown in Figure 4 .and incorporating means operable external 'of the valve chamber for varying the flowof pressure fluid through the valve.

vFigure 6 illustrates an alternate form of spring valve which may be substituted for the valvs illustrated in Figures 4 and 5 Refer-ring `to -Figure l, there Ais' shown a drive shaft il fixed to a hollow flywheel assembly 2 adapted to rotate within aV-casing 3. Flywheel 2 carries an ihternlal annular web 2a on each `side 'of which and completely within the flywheel isa pair of lluid pressure applied oi' operated clutches. The front clutch `A is composed 'of a hub 4 `splinetl to a driven shaft 7 `and carrying a clutch wplate element 5 adapted to be pressed against the vfront l'sur-face lof web 2a by means of an annular `piston 6. 'Piston 6 is 'actuated by lluid pressure applied to annular gcylihdiical space 22 through passage 462, and controlled by valve 99. Pressure is admitted to valve 99 yfrom lpipe'll in gland 5,9, through passages 60d-, 60h and 60e. The rear clutch B comprises a similar hub 9 spliiied to a hol-low driven shaft 11 and carrying aclutch plate 8 adapted to be pressed `against the rear surface of web 2a by an annular piston 9,. Piston 9i`s actuated by fluid pressure applied to annular cylindrical space 24 from pipe 66, through delivery passage 65 and pipe 66 in gland 59. Passage 65 communicates through passage 65a to passage 65b, the iluid pressure being admitted to cylinder 24 through passage 65C. Exhaust lluid through passages 96 and 97 is directed back to th'efpimp sump. The control of uid pressure to pipes 60 and 66 may be brought about in any conventional manner as by means of a thimble valve adapted to selectively con'- nect the pipes to a fluid pressure source or to cut both pipes off from the uid pressure source. Itwill be clear that when clutch A is energized, torque is transmitted from shaft 1 to shaft '7, and when clutch B is energized, torque is transmitted from shaft 1 to shaft 11.

Valve device 99 is mounted in drilled passage- 90 in 5- the flywheel body and is a speed responsive device for regulating the magnitude of the line 9 pressure applied to piston 6 through passage 62. Details of the valve 'are discussed more fully hereafter.y Valve 99' may be of similar structure to regulate pressure applied to pisi?"- ton 9 through passage 65 and annular space 24. Various modifications of the valve 99,-any one of which -may be used, as desired, in place of valve 99 are illustrated in the accompanying gures hereafter described in furf Valves 99 and 99 are permitted to vent var- --i ther detail. iably to exhaust through ports 96 and 97, respectively.

To counteract the clutch-binding effect of high centrifugal forces on the fluid in cylinders 22 and 24 of engageable clutch mechanisms A and B, the clutch pisy tons are associated with counterbalancing centrifugal means comprising a series of circumferentially spaced pivotal Weights. As shown in Figures vl and 2, each weight 80 is pivoted at 84 on the rim of an extension plate 82 of piston 9 and has a claw 81 engaging the outer rim of piston 6. Weight 80 is engaged at 85 by the outer `f i In this way, by proper pro- 'l As previously indicated, clutches A and B transmith" drive to coaxial shafts 7 and 11 which connect the clutch mechanism to epicyclic gearing behind clutch casing 3. The gearing comprises a front unit R and a rear unit L.

Inner shaft 7 carries two sun gears 10 and 15, the formerv meshing with planet gears 14 mounted on carrier 13 attached to shaft 11 and which also mesh with ring gear 16 of carrier 20. Sun gear 15 meshes with planet gears 17 mounted on carrier 20 and which also mesh with ring gear 19 on drum 13. Front carrier 13 has'a drum 12 adapted to be engaged and held by a' brake bandL 25, and drum 18 is adapted to be engaged and held by a brake band 30. Rear carrier 20 is attached to the nal load shaft 50.

By means of this gearing and the clutches, it is possible to obtain three forward gear ratios and one reversev ratio as follows. In neutral position, clutch A is'engaged and both brakes 25 and 30 are disengaged.` For low gear, clutch A and brake 30 are engaged. Drive is then from shaft 1, clutch A, shaft 7, sun gear 15, planet gears 17, carrier 20, and shaft 50.

For second gear clutch A is released and clutch B is engaged while brake 30 remains engaged. Drive is then from shaft 1, clutch B, shaft 11, carrier 13, planet gears 14, and to both sun gear 10 and ring gear 16. Sun gear 10 drives shaft 7 and sun gear 15 at a higher speed than in low gear; while gear 16 drives carrier 20 carrying planet gears 17 which engage with sun gear 15.` The result of this splitting and compounding of the drive is to rotate shaft 50 at a higher speed than in low gear, for a given engine speed.

For top gear, brake 30 is released and both clutches 4 A and B are applied. This locks the entire gearing together so that it rotates as a unit at engine speed, giving a direct drive of output shaft 50.

For reverse drive band 30 is released, band 25 is engaged and clutch A is energized. Drive is then from shaft 1, clutch A, shaft 7, sun gear 10, planet gears 14, ring gear 16, carrier 20, and shaft 50.

The mechanism for operating brakes 25 and 30 is shown in Figure 2 where part of brake 25 is cut away to show brake 30 and its mechanism. Each of the mechanisms is operated by fluid pressure under the control of valve devices which coordinate the operation of the brakes and clutches, as is well known in the art.

The band of brake 25 is anchored at one end by a rod tting in a notch 25a and is operated at its other end by a rod 26 fitting in a notch 25b on the band and another notch 27a on a lever 27. The lever is pivoted about a rod 37 supported in a suitable bracket 38, and its upper end is moved by a rod 28a on a piston 28 in a cylinder 29. The piston is moved against a release coil spring 31 when pressure is applied to the cylinder through pipe 29a.

The band on brake 30 is similarly arranged and operated. It is anchored at one end by a rod tting in notch 30a and operated at the other end by a rod 32 fitting in notches 30b and 30e, the latter being provided in lever 33 which is moved by piston stern 34a on piston 34 in cylinder 35. Pressure applied to pipe 35a moves piston 34 against release coil spring 36 to apply the brake.

In Figure 3 there is shown a schematic diagram of control for supplying fluid pressure to cylinders 22, 24, 29, 35 as desired.

Pipes 60 and 66 of Figure 1, as well as pipes 29a and 35a of Figure 2 lead to a valve control mechanism C adapted to selectively direct fluid pressure to any one of the pipes individually or in combination as may be desired, such valve controls being well known in the art. Pump P pumps fluid pressure from supply sump S throughV pipe 67 to selector control valve housing C containing suitable valving (not shown) for selectively directing fluid to pipes 29a, 35a, leading to cylinders 29 and 35 and to pipes 60, 66 leading to cylinders 22 and 24. Fluid pressure from cylinders 29 and 35 exhausts through passages 33 and 33 respectively, while fluid pressure from cylinders 22 and 24 is permitted to exhaust through exhaust passages 96 and 97. The exhaust fluids are directed back to sump S.

Theconstruction of Figure 4 represents a usage of the valve construction of the invention applied to the clutch mechanism of Figure 1. The radial drilled space in flywheel housing 2 acts as the valve chamber, the external- 1y located valve inlet port 100 being connected through the proper passages to the clutch chamber and to a source of ilid pressure of unvarying pressure level, or variable as needs require. The inner passage 96 leads from the valve Abore to exhaust space, or to the spent pressure reservoir.

Port 107 leads to passage 62 of Figure 1, which in turn communicates with the servo cylinder for actuating th clutch 5.

The outer portion of the bore 90 is closed by the screw plug 102 threaded into the flywheel body 2 of Figure l and is cross drilled at 103 for registry with the port 100, being centrally drilled at 104 through the extension 102a which acts as a guide for spring valve 105, fitted with `weighted plug 106 at the inner end.

Under rotation of the ywheel 2, the turns of the spring valve 105 may remain open until the rotational speed reaches a value at which they are compressed and the ow of fluid is restrained, and therefore there is a rise of pressure inside the turns of the spring valve 105, as the plug 106 under ycentrifugal force, moves toward the position shown in Figure 4a, between which there is variable exhau'st.

The fluid which formerly owed out through the elon- "arresto gated wide aperturesof spring valve 105 is new restrained to 'ow through a much srna'lller space byslrinlageAv of the interstitial areaslbetween the compressed spring' coilt'u'rns, as well as by reason of the turns effective tl provide luid passage becoming less in number as the turns' compress radially beyondthe effect-ive pressure relief space of the c harnber' At maximum' speed effect, the spring valve s is' fully compressed', and4 the upper face cf the plug 106 seat's against' this matching seatof `the hollow spindle 10221, exposing" pressure area of smaller extent. Upon fa'll of speed or rise of' effective pressure' in the passages connected to 100, the plug 106 becomes'u'nseated' andthe variable leakage action of valve 1'05 isi restored. If the external Vcontrols affecting the' value of the' pressure head on" tlievalve 105 and plug 106' arels'o manipulated, a controlled rise of such pressure could be etective to open valve`1l05 against the speed eifect,` and cause a drop i'n pressure sufficient to' diminish the holding. pressure' on the clutchi 5 of Figure 1. Su'chpre'ssure rise can onlyfunction up tothe maximum ori'ce capacity of the' relief passages, such as 96', however, so that the designermay uti'- lize the latter effect to prevent `undesired high pressure rise from slipping the clutch: VTlzie'lpress'ure fed to port 1:00-` as" provided; by thepurnp` P of Figure 3, may for example, be at 80 pounds to the square inch, and supplied lin such volume that the' clutcl'r 5of Figure 1l |will be fully engaged when the leakage of spring valve 105 is reduced below an effective orice area of 0.0035 squarel inch, for example. From this point on, with increaseofv speed, the spring valve 105 may' fully compress as noted abovel and come 'to'rest' with the plug 106 seated, so* that no leakage whatever occurs. In practice, a small amount of continuous leakage is` preferable, by whichA plug 1'06 would not ever block the orifice except at excessive speeds, inome'ntarily reached.

The radially outer face of the plug element 106acts as a pressure responsive valve seat surface, so'that the pump pressure and trapped pressure tend to open the turns of the spring valve 105 andI relieve' the line 1500.

Due to the fact that the spring wire is Aof circular section, the out flow velocity between close' adjacent turns tends to accelerate while the actual orifice pressure at" a point between two adjacent turns rises, tending to hold them open by fluid pressure elongation of the body of the spring valve 105. This characteristic tends to blast free small particles of dirt or foreign matter which ordinarilyl cause trouble in fluid pressure valving, andthe fact that there are many minor readjustments of the forces at work in a short time period adds further to the' self-cleaning and pressure stabilizing action. It will be noted that toward the end of travel in which the spring valve 105 is `nearly closed, a component of the luid pressure is tending to stretch or expand the spring diametrally and therehy decreases its overall length in contrast to the pressure acting on the upper face of the 'plug 106 which gives an effect cr cushioning towardy the end c'f the' travel.

The structure shown in Figures 4 and 4a en'lltodie's'A a weighted plug element 106, which is free to turn about the spring valve axis without restraint. The upper end of the spring valve 105 may be staked into the plug 102 so that these parts are removed as an assembly, although this is not necessary, except for special design reasons to be dealt with further.

The chart of Figure 4b provides a representation ofthe operation of the structure of Figures 4 and 4a, showing increase of speedv compared with rise of pressure in the pressure passages connected to line 100, indicating the pressure loading on the clutch 5 of Figure l, in full line at X.

In Figure 5 a different arrangement of the regulating spring valve is given, the higher lline pressure being applied external to the springl turns and the lower-pressure existing inside the spring valve when the spring is cornpresse'd. The spring element 105 isf retained in chamber 90 by a screw plug 11012` with extension 10221' acting as a guide fer fue spring' valve rds' compressed by the radial force of sliding plug 106 weighted to respond to centrifugal: force. At low speeds" cr nvwhcel 2, there is free now through the turns` of the spring 1'0'5 from pressure pas# sage 60C tio reliefA passage 101 which exhaust to snmp; With increase of speedA the valve 1'05'i`s compressed as shown in Figure 5a. The weighted plug 106 is drilled out centrally as at" 106:1. This form of combination valve is somewhat' less sensitive to line pressure variations `Eine: it is exposed to high pressure only over a' small rin'gshaped area near the cylindrical periphery. With respect to the outlet pressure, plug 106V is partially balanced. At excessive or extreme' speeds the plug 106, by design, may be made t'o ab'ut the' inner end of boss 102:1- of plug 102, thus aiding the blocking of bleed' leakage from 60a` to 101. The plug `10'6 need Ybe only a running fit in bore 90. Should'` the spring ends' be' staked into the plugs, or recessed so' as to not rotate freely, allowance is made for rotation of plug 106; Should' the upper spring end be recessed in a hole in plug 102, or otherwise sol retained, and the plug 106 prevented from rotation, the spring may be placed under a pre-lbad or in pre-stressed condition by winding ofV th'eturnswith rotation of the plug 102 toa predetermined angularloek point. Variations of such andarrangern'ent are illustrated in Figures 5a, 5b and 5c. This adjustment permits accurate setting after installation, for desired` speed response characteristics, as against the irlvolvcd process of pre-calibration, since the physical factors of minor orifice effect and friction of plug 106 in the bore 91V may vary sufficiently to make accurate setting otherwise difficult.A For'su'ch a purpose, the plug 106 may have an extension lug' I06b` riding in a radial slot 106C Vas indicated in dashed linein Figure 5a, or it may be guided' and held against? rotation on its own center by an arrangement as shown in Figure 5c, where the inner end of a stem- 107 on the plug 106 is milled to square section to match with the square inner section of a raised boss 108. The nt of these square sections is not critical since the fluid pressure in passage 106a is the same as be'- low the'plug. Figure 5b is a plan view of the top of the plug 102 as used for preeloading the element 105, setscrefw 11-6 serving to hold a pre-set adjustment. A sl'ot 102e' is provided in plug 102 so that the tension of spring 105 may be readily and quickly adjusted as desired.

In` Figure 5d, the construction is like that of Figure 4 b'ut the plug 10d is tapped for overcontrol rod member or element 152 which may kbe utilizedl to vary the positionof plug 106 in valve chamber 90 manually or automatically.

Figure 6 shows an alternate embodiment of my invention in which a single pressure regulator valve may be substituted for the pair or regulator valves heretofore described. ThisV alternativeembodiment is adapted t`o be positioned in the hydraulic system between the pump P and the' manually operable' selection valving C of Figure 3*, and the individual pressure regulator valves 99 and 99 will therefore be omitted. Speciiically, the alternate pressure regulator will be positioned in line 67 of Figure 3, while lines 6:0 and 66 of Figure 3 will be connected directly to cylinders 22 and 24, respectively.

in Figure 6, there is shown a centrifugal valve form of pressure regulator or governor having a shaft driven by meshing Worm gears 151 and 152 from the shaft 50 of Figure l. Shaft 150 is supported in housing 100g by means of bushing 153, and has xed to its upper end a valve body 154 drilled for aV slidable rod 155, and bored to form space 156. Rod 155 has axed thereto a calibrated weight 157 at the left end and the rod is fastened to aretainer member 158 at its right end. The rotation of shaft 150 and body 154 tends to increase the kinetic force of weight 157, causing the weight to move outwardly radially. A spring 160 is closely recessed against the body 154 at one end, and at the other end iit's closely into a formed ledge in retainer 158, the spring A160 acting to resist the outwardly acting centrifugal force of weight 157 on rod 155.

` The housing 100g is drilled for connections 68 and 69 so that pump pressure from pipe 67 enters at 68, while pressure fed to the intake side of the selector valve C is conducted through 69. Shaft 150 is cross-drilled at 161 to register with connections 68 and 69, the bushing 153 also being so apertured. Shaft 150 is centrally drilled at 162 to intersect with cross drillings 161 and is Vopen to bore space 156 of body 154.

Assuming that the pressure regulator is disposed in Athe hydraulic system in line 67 of Figure 3 between the pump and manual selector valve and that shaft 150 is not rotating, the pressure in bore space 156 is exerted to stretch spring 160 to the right and to leak oll or exhaust the pressure of the system to the exhaust space and back to the sump, the pressure in the system thereby being maintained at a low net pressure level determined by the ,capacity of the supply pump and the spring turn orice dimensions. i Rotation of shaft 150 applies centrifugal force to rod 155, to hold retainer 158 toward the left and compress the turns of spring 160, thereby restricting the leakage through the spring turns and accordingly raising the pressure of fiuid fed to the selector valve and to the servomotors An equilibrium condition of centrifugal force as against fluid pressure tending to relieve the line pres- ,sure within the system is reached for each steady rotational speed of shaft 150. The adjacent turns of spring 160 are therefore utilized as a valve having a long seat with respect to the stroke of the valve action.

At high vehicle speed ranges of shaft 150, as indicative of high vehicle or output speeds the permitted leakage is at a minimum, this value being calculated for and calibrated so as to permit a small substantially continuous .vent flow for the system such that the oil body maybe constantly circulated for desired cooling requirements.

The valves of Figures 4 and 5 with the loose plug con- .struction of Figure 4 whereby the plug is spaced from the valve bore 50, and the running t of the plug in the bore of Figure 5 arc free from sticking at either end of the plug travel, and may operate continuously and indefinitely without wear or loss of design characteristics. It is especially dif'licult for dirt or foreign particles to lodge in the interstices of the spring valve turns due to `velocity increase effects in the flow. For example, if in .the Figure 4 embodiment a metal fragment is lodged .between adjacent turns, thereby holding them apart to create leakage, the sealing of the adjacent turns by llexure of the spring material under axial pressure causes the leakage flow to build up in the turn area directly adjacent the fragment so that it is dislodged quickly by the rise of velocity flow and pressure. in this manner the device is self-cleaning and particles of larger diameter than the normal turn spacing may be squeezed through with facility. When clogging occurs, the quick and simple removal of plug 102 permits rapid examination of the entire assembly, repair and replacement.

' In the Figure 4 embodiment, a lateral clearance space has been shown between the cylinder -wall 9u, plug 106, and the external surface of the turns of spring valve 105. .it will be understood that under rotation, the conditions of acceleration cr deceleration will tend to cause the spring 10S and plug 166 to swing away from the bore centerline or radial axis and to incline so as to lag or vlead at the inner end where the plug 106 is located. This vinertia effect results in bowing or distorting the spring slightly, opening the turns on one side or another, but diminishes as speed increases, since the moment arm of valve 105 and plug i706 about the fulcrum point of the retainer guide i6-Zia is lessened as the spring becomes shorter. The same effect occurs under deceleration and is regulated in design by the masses, moment arm, and lforce resistance value of the spring valve, to control the permitted bowing of the spring.

In the FigureS .embodiment the clearance space of plug 106 forms a close running ft so that the inertia effect due to acceleration or deceleration is provided only in the body of spring 105. The turns of spring 105 may be designed tollie so close to cylinder wall that the inertia effect is practically absent.

The result of this feature, however, is to enable the designer to proportion these effects to suit the desired drive and torque capacity requirements of the brakes and clutches, and'also to introduce a speed plus inertia governing action into an automatic or manually controlled shift ratio pattern.

If, for example, the driver is accelerating in low gear from an engine idling speed of about 250 R. P. M., as illustrated in Figure 4b, the net valve closure under speed and fluid pressure effect may cause the clutch 5 of Figure l to increase loading according to the engine speed-pressure curve X. The inertia effect may, by design, cause the clutch loading pressure to rise more gradually. The bowing of the spring permits more pressure to leak out than would leak if the acceleration were more gradual, lgiving a pressure-speed curve as illustrated at X of Figure 4b. This acceleration-deceleration effect results in smoother clutch engagement and reduced shock loading.V

Upon deceleration, as by retarding the vehicle engine throttle or by' braking the vehicle or both, from say about 2000 R. P. M., or around 20 miles per hour, the plug and element 105 of Figure 4 can swing off the spring axis, and as the speed falls off the effective moment arm increases, thereby increasing the inertia effect. While the net decelerative force falls, the proportional effect of inertia persists; whereas, under acceleration the inertia effect dies out with the rate of increase of acceleration due to the shortening of the moment arm as the spring is compressed and as thelturns of the spring progressively move outwardly past the end of guide member 102e.

The provision of an inertia effect superimposed upon a speed effect to oppose the same decreasingly with increaseiin speed but rising with increase of acceleration, and to provide an inertia effect which is created by deceleration but which tends to remain while the speed is diminished due to the varying moment arm action described above is believed novel.

Since in motor vehicle operation sudden increases in acceleration or deceleration tend to produce shock loads on the driving parts and couplings; it is often advantageous to ameliorate these effects by some form of limiting control calibrated to suit the torque forces to be dealt with, and the spring valve arrangement herein for providing a predetermined inertia factor control as outlined above, introduces a cushioning action in the cyclic torque capacity actuation system for the clutches.

Having disclosed various modifications of a spring valve pressure regulator and the manner in which it may be incorporated in a transmission control system, the invention intended to be protected is set forth in the following claims.

I claim:

1. A governing mechanism for controlling apparatus to be governed comprising a rotating body, a chamber in said body, a coil spring in said chamber having a series of successive, open coil turns, a weight member disposed in said chamber and connected t0 compress the spring turns with respect to a portion of the body under rise of rotational speed and provide a variable flow through the said turns, a fiuid pressure supply passage connected to said chamber exterior of said coil spring, an exhaust passage from said chamber operative to receive pressure fluid passing through the coil turns of said spring, a pressure delivery passage connecting said chamber to said apparatus to be governed, a passage through said weight member for permitting fluid flow from the interior portion of said coil spring to said exhaust passage, said weight being movable in response to variation in speed of rotation of said body to' vary the space between adjacent coils of said coil spring, the pressure supplied to said chamber through said pressure supply passage being operative upon said weight to oppose the centrifugal force eiiect of said weight in determining the relative spacingy of adjacent coil turns of said coil spring.

2. A centrifugally actuated pressure control valve comprising a rotatable valve body having a valve chamber therein, a coil spring disposed in said chamber, said coil spring being lxed at one end and free at the opposite end, uid' pressure supply, delivery and exhaust ports associatedl with said chamber', a weight member secured to the free end of said co'il spring so as to require 'uid ow through the coil turns of said coil spring from the said supply, anda passage through said Weight member for permitting iluid Vflow from the' interior portion of said coilV spring t'o said exhaust port, said weight member and said spring being variably movable in response to' Variation in speed of rotation of said valve chamber to vary the; space between adjacent coil's of said spring.

3'( centrifugally actuated pressure control valve comprisinga valve body adapted for rotation about a given axis of rota-tion, a valve chamber in said body extending perpendicular to said axis of rotation, a coil spring mounted to expand and contract in said chamber having a xed endy and afree end, said coil spring extending perpendicular to said axis of rotation; a weight member lixed to the free end of said coil" spring so as to require fluid how through the coil turns or said coil spring, and uid pressure supply, delivery and' exhaust ports associated with said chamber, saidy supply and exhaust ports being positioned with respecttosaid coil spring such that fluid i'ow from' said supply to said exhaust port is directed between the coils of said eoilspring, said weight member beingmovable in response tovariation of speed of rotation o saidbody to' vary the spacing of adjacent coils of said' coill spring with respect to each other, and correspondingly vary the degree of outiiow to the said exhaust pol-t,.- the- Huid pressure admitted to said chamber through saidpres'sure supply port acting upon said weight member in opposition` to the centrifugal' force effect of said weight member.

4. centrifugally actuated pressure control valve comprising. a rotatable body, a valve chamber in said body, i

af coil spring'valye in said body having a iixed end and al free end, al weightA member xedf to the free endl of said coil; springvalve adapted to restrict the" free end*- turns of said'` spring'` valve against fluid flow through theV coill turns of. said valve;- an: exhaust passage in said body, andn fluid pressure supply and delivery ports connected to at space associated Withsaid coi-l1 spring, said weight being movable` in response to variation in the speed of rotation of said:` bodyto vary the spacing between' adjacent coils of said: coil springtol vary the rate of fluid flow through the coilt turns` of the saidspring: valve fromI said= huid pressure supply to said exhaust passage, the fluid pressure admitted to the space within the turns of said coil` spring being applied to said weight member inopposltion to` the centrifugal force eiect of said weight member upon said spring valve.

5. A centrifugally actuated pressure control valve cornprising a vrotatable body, a valve chamber in said body, acoil spring valve in' said chamber having a` xed end and a free en'd, a Weight member fixed to the free end of said coil spring valve, said weight member being effective' to divide'- said chamber into higher and lower pressure portions, respectively, uid pressure supply and delivery portsf connected to the higherl pressure portion of saidl chamber with respect to said coil spring valve', an

exhaust port connected to the lower pressure portion of said chamber, and a passage for permitting fluid ow from the lower pressure portion of said chamber to said exhaust por-t, said` weight being movable in response to variation in speed of rotation of, said valve chamber to vary the spacing between adjacent coils ofsaidcoil spring arresto valve, the fluid pressure in. said higher pressurle portion of said chamber being operative upon said weight member to oppose the centrifugal? force effect of said weight member upon said coil spring valve.

6. A centrifugally actuated pressure control valve device comprising a body subjectv t'o rotary motion, a valve chamber therein', a plug member closing oli one end' of said valve chamber', a nipple on said plug extending into said valve chamber, a coil spring valve having one end thereof secured `to said plug positioned with a portion of its coils extending intermediate said plug and the end of said nipple andl a portion of its coils extending inwardly past said' nipple to present a free end in said valve chamber, a weight member carried by the free end or said coil spring valve eiiective under rise' of speed to compress said spring valve and thereby to' block off the successive turns thereof against uid flow through the coils of the spring valve, and fluid pressure supply, delivery andv exhaust ports in said' body positionedI with respect toA said coili spring valve such that lli'l'id pressure flowing from said pressure supply tol said exhaust port is directed between the'coils of said:A coil spring valve, said weight member being movable in response to variation of the rate of rotation or" saidE body to vary the relative spacing adjacent coils of said spring to vary the rate of uid ilow to said exhaust port, the huid pressure admitted to said chamber through said pressure supply port being operative upon said weight in opposition to the centrifugal force effect of saidv weight uponsaid coil spring valve.

7. A centrifugally actuated' pressure regulator valve comprising a rotatable valve' body having a valve chamber therein, al plug member blocking 0E one end of said valve' chamber', a* nipple onsaid plug extending into said valve chamber, a valve seat onsaid nipple, fluid pressure inlet and delivery passages in said plug, a coil spring valve` in saidcliani'be'r positioned with aY portion of its coils extending radially inward? of said body and adjacent said nipple and a portion of its coils extending similarly into* said chamber beyond the end' of said nipple to present a movable end' in saidchamber, a passage in said nipple connecting the interior of said coil spring to said pressure: supply' and delivery passages, an exhaust port in said valve chamber, a Weight member secured to the movable end of said coil springvalve for preventing uid how through the' movable endl 0E saidy valve, said weight member' being'. movable in' response to variation in the -rate of. rotation of said valve bo'd'y to vary the spacing between adjacent coils of sai'd coil spring valve, and a valve seat` on said weightl adaptedV to register with said nipple valve seat:r under extreme centrifugal force, said exhaust'p'ort being: positioned'. tor receive uuid passing intermediate the: coilsf of said spring.

8. A- centrifugally actuated pressure regulator valve comprising. a valve bodyy subject to rotary motion, a valve chamber: in said body; a: plug: member at one end. of said valve chamber, ar coil spr-ing` valve in said chamber having. one: end thereo seated upon said plug, a weight-member` adapted to` move' the other end of said coil spring valve',` said weight. member beingzpositioned in said chamber for. linea-r motion thereinA and xed against rotary motioni witht respect to saidv chamber, said plug being adapted to bei rotated with respect to said chamber to vary thetensionof saidt coil. spring valve, and Huid-pressure supply, delivery andi exhaust ports associatedl with said valve chamber, said supply and exhaust ports being positioned` with respectV to said coil spring valve such that uid. pressure` passing from said supply to said exhaust port is; directed through the coils ot said valve, said weight beingA movable with respect to said end plug in response to variation in t'the speedv of rotation of said valve body toy vary the space between adjacent coils of said; coil spring, the fluid pressure supplied to said valve through said', pressure supply port being applied lto said Weight in opposition tothe centrifugal force effect of said'weight upon the coils' of said' coil spring valve.

9. A pressure control valve comprising a rotatable body, a valve chamber in said body, fluid pressure inlet, delivery and exhaust ports associated with said valve chamber, a coil spring valve disposed in said chamber having one end thereof fixed at one end of said chamber and a movable end extending into said chamber and spaced from the walls of said chamber, and a weight member secured to the movable end of said coil spring valve effective to compress said coil spring valve as the speed of rotation of said body is increased, said weight member also being eective during periods of accelera tion and deceleration of said body to bend said coil spring valve out of normal alignment so as to vary the spacing between adjacent coils of said valve, said inlet, delivery and exhaust ports being positioned with respect to said coil spring valve such that fluid passing from said inlet port to said exhaust port is directed between the turns of said spring.

10. A centrifugally actuated pressure regulator valve comprising a rotatable valve body, a valve chamber in said body, uid pressure supply, delivery and exhaust ports communicating with said valve chamber, a coil spring valve disposed in said valve chamber having one end retained by said body and a movable free end extending into said chamber, and a weight member xed to the free end of said coil spring valve, said coil spring valve being disposed in said valve chamber such that inertia forces acting upon said coil spring valve will bend said coil spring with respect to the axis of said chamber during periods of acceleration and deceleration of said valve body, the inertia eiect of said valve spring acting in opposition to the centrifugal eiect of said weight during periods of acceleration of speed of rotation of said valve body and said inertia effect of said valve spring acting in assistance to the efect of said weight during periods of deceleration of the speed of rotation of said valve body, said uid pressure supply, delivery and exhaust ports being positioned with respect to said coil spring valve such that uid passing through said valve chamber is directed between the turns of said coil spring valve.

1l. A centrifugally actuated pressure control valve comprising a rotatable valve body, a valve chamber in said valve body, tluid pressure inlet, delivery and exhaust ports communicating with said chamber, a coil spring valve disposed in said chamber, said coil spring valve having sectional abutment at one end of said chamber and having a movable end extending radially into said chamber and spaced from the walls of said chamber, a weight connected to the movable end of said spring effective to prevent iiuid flow through the open end of said spring, said weight being movable in said chamber to compress said coil spring valve upon increase of speed of rotation of said valve body, said spring valve presenting a variable moment arm decreasing in length as said coil spring is compressed and increasing in length as the coil spring is extended, said weight being effective to compress said spring upon increase in speed of rotation, said spring being positioned in said chamber such that inertia forces acting upon said spring will bend said spring out of radial alignment during periods of acceleration and deceleration of the speed of rotation of said valve body, said inertia effect being superimposed upon the speed effect of said weight to oppose the same decreesingly with increase of speed of rotation of said valve body and to oppose said speed elect increasingly with increase in acceleration of said valve body, said inertia effeet acting in assistance to said speed effect during deceleration ot thc speed of rotation of said valve body and increasing in eicctiveness as the rate of deceleration of said valve body increases, said inlet and exhaust ports being positioned with respect to said coil spring valve such that iluid passing from said inlet port to said exhaust port is directed between the turns of said coil spring valve.

l2. ln power control devices in combination, a mechanism to be variably controlled, a uid pressure actuator for said mechanism operative to provide such required variable operation, a iluid delivery passage providing variable uid pressure to said actuator for said mechanism, a fluid pressure supply source, a pressure supply passage leading from said source, an exhaust space, a rotating control device including a valve body and a valve bore in said body, uid connections for said passages and said exhaust space in said body, and a centrifugally operable valve located in said bore effective to vent variably the pressure of said supply passage to said exhaust space and thereby cause the pressure of said delivery passage to vary in accordance with changes of speed of said device, said centrifugally operable valve including a coil spring member located in said valve bore having a series of coil turn portions effective to be compressed or elongated in accordance with such speed variation and thereby provide the said variable vent action through the said turns of the spring.

13. A centrifugally actuated pressure regulator valve device comprising a rotatable valve body operated at varying speeds of rotation, a radially disposed valve chamber in said body, a fluid pressure supply connected to said chamber, a valve weight member having a portien movable radially within said chamber, a pressure delivery passage operatively connected to said chamber, an exhaust space, a coil spring connected to said weight member and normally having open coil turns operative to permit ow passage of uid from said chamber to said exhaust space related to said member such that upon rise of rotational speed of said body, the coil turns are caused to be variably closed and thereby variably restrict the said flow through said turns in accordance with said rise or" speed and thereby operative to cause a corresponding rise of pressure in said delivery passage.

14. In a change-speed transmission which includes a plurality of step-ratio gear trains, and plural clutches adapted to be engaged in a selective pattern of engagement for establishing drive by said trains between driving sind driven shafts, a source of fluid pressure, control valving operative to direct the pressure of said source for actuating said clutches in said pattern, fluid pressure operated actuator means for said clutches, fluid pressure passages for connecting said source and said valving to said means, and a regulating valve located in at least one of said passages, said valve including a coil spring capable of elongation and compression and responsive to the speed of said driving shaft to elongate or compress for varying the ow between the turns of said coil spring and thereby causing the clutch actuating pressure of said one passage to rise with the said shaft speed.

15. In the combination set forth in claim 14 the subcombination of a second regulating valve means including a second coil spring in another of said passages likewise subject to driving shaft speed and operative in the same manner as described for said first-named valve to cause the actuation pressure of its clutch passage to rise with rise of said shaft speed.

16. In power transmitting mechanism, a friction clutch driving member, a driven member to be engaged with said driving member, a clutch actuator operable to engage the clutch under the application force of fluid pressure, regulating means operable to provide variable exhaust for the clutch-applying fiuid pressure including a coil spring valve mounted to rotate with said driving member and having its axis radial with respect to the rotation of the clutch, a weight member operatively associated with said coil spring, the open turns of the coil spring being variably closed by action of centrifugal force on said weight member in accordance with the rise of speed of said driving member thereby to restrict the variable exhaust action, and a valve chamber surrounding said valve and spaced laterally from the sectional coil dimension of the coil spring valve so as to permit its deflection from its 13 radial axis under inertia force and provide a distortion of the coil turns for increasing the exhaust action.

17. In power transmissions, driving and driven shafts, wherein a change-speed gear train is adapted to couple said shafts for drive at differing speedrratios, having a first friction clutch operable to establish initial drive and continue drive, of the driven shaft through the said train at a given low speed ratio, and having a second friction clutch operable to engage and transmit a different speed ratio from that established by the rst clutch through the said train while the rst-named clutch is being released from driving, a uid pressure actuation system for both said clutches including a pressure supply and directing valving to select drive by one or the other or both of the clutches, the selected clutch being engaged and actuated by the fluid pressure directed to it by the valving, and a speed responsive valve subject to centrifugal force of a valve member rotating with said engine shaft and operable to regulate the uid pressure force directed to said second clutch during the interval when the said firstnamed clutch is being released, said valve including a coil spring valve element caused to compress its successive coil turns variably with rise of speed of said engine shaft, and thereby cause the clutchpressure force to rise with such rise of speed.

18. In the combination set forth in claim l2, the subcombination including a pressure space within the turns of the coil spring and connected to said supply passage, a closure member of said valve for one end of said spring, and a pressure area of said closure member responsive to the pressure of said passage for modifying the centrifugal speed response variation of said valve.

19. In the combination recited in claim l2, the subcombination of mechanical connection operative to apply an overcontrol force to the said valve and to vary the venting action from that otherwise determined by the centrifugal operation of the valve in accordance with changes in the speed of rotation of said mechanism.

20. In the combination recited in claim 13, the further combination of an overcontrol element operative by external connection to shift said member portion to predetermined positions for selective regulation of the flow between the coil turns of the spring other than determined by the rotational speed of said body applied to said portion.

- 2l. In power drive controls, in combination, a control member, an engageable clutch element, a fluid pressure actuated piston and cylinder structure operable to apply engaging force to said element, a uid pressure supply, a pressure delivery connection to said cylinder, a control valve operated by said control member for selectively controlling the operation of said piston upon said element by selective control of delivery to said cylinder from said supply through said connection, an exhaust space, a regulating valve device in said connection including a coil spring with turns operative to vent the pressure thereof variably to said space and thereby vary the effective pres sure acting upon said piston for engaging said element, a coil spring portion of said device having open turns through which the pressure of said connection is variably vented to said space, a rotating valve body mounting said valve and said spring, and a centrifugal force responsive element rotating with said body and operative by the centrifugal force acting upon thel said element .to vary the spacing of said coil spring turns in accordance with changes in the rotating speed of said body.

22. ln clutch controls forpower transmission mechanisrn, which have in combination, a rotatable driving member', a driven member, a clutch for said members, uid pressure operable means for causing actuation and engagement of said clutch, a pressure delivery passage for said means, selector valving for controlling the pressure delivered by said passage to said means, a member for shifting said valving to render the said means opera- 'tive and inoperative, the combination of regulating means driven by said driving member for controlling the mag-l nitude of the pressure in said passage and acting upon said fluid pressure operable means, said regulating means including a rotatable casing, a valve bore in the casing, a coil spring valve element movable radially with respect to the axis of rotation of said rotatable casing in said bore and a weight member subject to centrifugal force and carried by said coil spring element, said valve element having open turns through which the pressure of said passage is vented more rapidly at one speed than at another speed of rotation of said casing.

23. In transmission mechanism having the combination of a power shaft, a load shaft, change speed mechanism between the two shafts for changing the speed ratios therebetween, a uid pressure supply pump, a pressure supply connection from said pump, ratio selector valving, a plurality of clutches embodied in said mechanism and selectively engageable in a pattern to provide different speed ratios, uid pressure actuators for each clutch and pressure delivery connections for. each actuator adapted to be connected to said supply connection by said valving to provide said clutch engaging pattern, the combination of coil spring pressure regulator valves located in each of said delivery connections operable to bleed off a variable quantity of the pressure delivered by said valving, said regulator valves each having arrotating body responsive to speed of rotation, each of said valves including a weight member subject to centrifugal force developed in said body by said rotation, each of said valves having multiple open turns which are variably opened or closed by action of the weight associated therewith to vary said bleed in accordance with changes in the speed of rotation of said body.

24. In power transmission, driving and driven shafts, a friction clutch for connecting said shafts, a fluid servo actuator for applying engaging force to -said clutch to provide unit speed of said shafts, an actuator conduit, a fluid pressure` supply system including a pressure source, valving for delivering pressure from said source to said actuator through said conduit, or for cutting ofi said delivery, and the combination of a pressure-varying regulator device for the pressure supplied by said valving to said conduit and said actuator, including a rotating valve chamber connected to said conduit containing a centrifugal relief valve which includes a coil spring and a weight member, the turns of said coil spring being variably compressed by centrifugal force response of said Weight member to vary the relief of the pressure of said chamber.

`upon increase in speed of rotation of said valve chamber to thereby variably increase the pressure supplied to said delivery port upon increase in speed of rotation of said valve chamber. v

. 26. A pressure regulator device vfor regulating the fluid pressure delivered from a source, said device including a rotatable valve chamber, a coil Spring valve disposed in said chamber, an inlet port in said valve chamber, a delivery passage leading from the chamber, an element movable to compress said spring valve in accordance` with the speed of rotation of the chamber l0 ,i11-

crease the pressure supplied to said delivery passage upon increase in speed of rotation of said valve chamber, said -spring valve and said passages being positioned such that uid passing through said chamber passes between the turns of said spring valve.

27. A device for regulating pressure supplied from a Source Qf. fluid under pressuresomptisns a Valve chamber positioned for rotational motion, a coil spring valve disposed radially with respect to the axis of rotation of said valve chamber in said valve chamber, an inlet port in said valve chamber, a pressure delivery port in said valve chamber, an element in said valve chamber movable radially with respect to the axis of rotation of said valve chamber by centrifugal force in response to rotary motion of said chamber for compressing said spring valve, and an exhaust port in said chamber, said inlet and exhaust ports being positioned with respect to the coil turns of said spring valve such that fluid passing through said chamber is exhausted between the turns of said spring, said spring valve being effective to increase the pressure supplied 'to said delivery passage upon 'increase in rotational speed of said valve chamber.

28. A device for variably controlling fluid pressure comprising a rotating valve chamber, an inlet port in said valve chamber, a coil spring valve disposed radially with respect to the axis of rotation of said valve chamber in said valve chamber, a centrifugally responsive element directly operative for varying the relative spacing of the turns of said coil spring valve, an outlet port in said chamber, said inlet and exhaust outlet being positioned relative to said spring valve such that fluid passing through said chamber is directed between theV coil turns of said spring valve.

29. A centrifugally operable pressure regulator device for regulating uid pressure comprising a valve chamber subjected to rotary motion, a plug member of said chamber including a nipple extendinginto said chamber, passages in said plug member and nipple adapted to connect said valve chamber to a source of uid under pressure, a coil spring mounted radially with respect to the axis of rotation of said valve chamber in said chamber with a portion of its turns intermediate Isaid plug and the end of said nipple and a portion of its coils lying inwardly of said `nipple in said chamber, a weight element in said chamber movable radially with respect to lthe axis of rotation of said chamber in response to rotary motion of said chamber for varying the relative spacing of said coil spring turns, an outlet port in said chamber positioned such that uid passing through said chamber to the outlet port passes between the coil turns of said spring.

30. A Acentrifugally operable valve means for regulating pressure comprising, a valve chamber subjected to rotary motion, a plug member including a nipple extending into said chamber, a valve seat formed on the inner face of said nipple, passages in said plug and nipple adapted to connect said chamber to a source of fluid under pressure, a coil spring in said chamber positioned with a portion of its coils extending outwardly around said nipple and a portion extending-inwardly from -said nipple into said valve chamber, a weight element in said valve chamber operative lto block olf the vfree end of said coil spring against fluid flow and adapted to compress said spring centrifugally 'in response :to rotary motion of said chamber, a valve seat formed on said weight adapted to register with vsaid yfirst-mentioned nip- -ple valve seat under-action of centrifugal-force, and an exhaust port in said valve chamber Ipositionedto receive fluid passing intermediate the coils of said-spring.

31. A device responsive -to centrifugal Vvforce for regulating 'pressure comprising 'a valve chamber subjected to rotary motion, a plug member permanently closing off one end `of said valve chamber, a second, movable plug member slidably positioned lfor-radialfmotio-n with respect to the axis of rotation of said `valve chamber in said valve chamber, a coil-spring ydisposed -in said chamber intermediate said plugs, van opening .in -a Ywall Aof said chamber .adapted .to be vconnected Ito ya ,source .of

communication between the space interiorof saidcoil Spring and:saidtlasrzstentieaedzagrt 32. A device responsive to centrifugal force for regulating pressure comprising a valve chamber subjected to rotary motion, an aiixed plug member in one end of said valve chamber, a reduced portion of said plug extending into said valve chamber and having a valve seat formed thereon, an opening .in said valve chamber providing communication between the interior of said chamber and a conduit, a second plug slidably positioned in said charnber'lfor' radial movement with respect to the axis of rotation of said chamber and fixed against rotary motion with respect thereto, a coil spring positioned in said chamber intermediate said' extension and said second plug, a valve seat 'formed on said second plug adapted to seat on said rs't-mentioned valve seat when said chamber is rotated above a predetermined speed7 said spring being retained by both of said plugs and said aiiixed plug being adapted to be rotated with respect to said chamber so as to vary the tension in said coil spring, a passage through secondmentioned plug providing communication between the space interior of said spring and the adjacent end of said chamber, and an exhaust port for uid passing through said passage.

33. A valve device for regulating fluid pressure including a valve chamber subject to rotary motion, inlet and outlet ports and an exhaust port in communication with said valve chamber, a coil spring valve disposed in said chamber for radial motion therein .with respect to the axis of rotation of said chamber and spaced from the wall thereof, an element responsive to centrifugal force for compressing .said spring, said spring valve being positioned in said chamber to permit a limited bending motion of said .coil .spring valve in response to variation of the rate of change of speed of rotation of said chamber, and said inlet, outlet, and exhaust ports being positioned with respect to said valve such that pressure fluid passing from said inlet port to said exhaust port passes between the turns of .said coil spring valve.

`34. A valve ldevice for regulating fluid pressure including a .Valve chamber subject to rotation, pressure inlet, outlet, and exhaust ports communicating with said valve chamber, a coil spring valve disposed in said chamber for radial .motion with respect to the axis of rotation of said chamber and Ispaced from the wall thereof, said spring having normally open turns, an element responsive to centrifugal force for compressing the turns of said spring, .the spring being positioned in said chamber such ,that the inertia Aeffect of said spring and said element .tends to bend isaid spring with respect to the axis ofsaid chamber yupon change .of the speed of rotation of the lchamber, said inertia effect acting in opposition to the ,effect ,of yincrease of said centrifugal force of said ,ele- .ment and said inertia effect acting in'assistance to said `centrifugal ,force ,responsive element upon decrease in the speed .of rotation of said valve chamber, said inlet, outlet, and exhaust ports being positioned with respect to .said `valve such that fluid passing through said chamber passes betweenvtheturns of said spring. Y

35. A valve device for regulating pressure including a valve chamber subject to variations in speed of rotation, pressure inlet, outlet, and exhaust ports communicating with said chamber, acoil spring disposed in said chamberforvradial ymovement with respect to the axis of rotation of said chamber yand spaced from the lateral walls thereof, .a weight element connected to Vsaid coil spring .alldmovablypositioned in said chamber so as tocompress said coil lspring variably with increase .of speed of rotation of said chamber, the variable moment arm .of the lspring Adecreasing in length as it is compressed and increasing in length `asl it is extended, said spring 1being `positioned in said chamber such that under acceleration .of such rotation speed the spring tends to bendhand under increase of the speed `of rotation of said Lchamber, the speed effect tends to oppose the acceleraftionfeect, lsaidlinertia effect acting in assistance to said speed .eifectupon deceleration of the speed'of rotation of said valve body and increasing in eiectiveness as the rate of deceleration of said valve body increases.

36. In speed-controlled mechanisms, the combination of a device to be governed in ac-cordance with governing changes in speed of a shaft, a pressure-applying member adapted to operate said device by variations of applied pressure to the member, a pressure supplying pump arranged to provide a steady source of pressure, a governor mechanism including a rotating valve body connected `to said pump and to said pressure applying member, said shaft driving said body at variable speeds, a iluid pressure exhaust passage in said body, said body having a Valve chamber therein a coil spring disposed in said chamber so as to require fluid low yfrom said pump to said exhaust passage through the coil turns of said coil spring, and -a weight arranged to move radially with respeot `to the axis of rotation of said valve body upon change of speed of rotation of said valve body and to compress the spring turns with rise of speed of said valve 18 body and thereby restrict the outflow of fluid through said `coil turns from said exhaust passage.

References Cited in the le of this patent UNITED STATES PATENTS 125,937 Cowles Apr. 23, 1872 342,275 Walters May 18, 1886 1,029,097 Atkinson June 11, 1912 1,189,697 Kasley et al. July 4, 1916 1,760,315 Nacket May 27, 1930 2,095,770 Sorensen Oct. 12, 1937 2,155,247 Warner Apr. 18, 1939 2,217,940 Bragg Oct. 15, 1940 2,325,814 Tyler Aug. 3, 1943 2,363,279 Anschicks Nov. 21, 1944 2,396,361 Browne Mar. 12, 1946 2,440,589 Kegresse Apr. 27, 1948 2,549,090 Hobbs Apr. 17, 1951 2,633,760 Kelley Apr. 7, 1953 

